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' De c. 15, 1 970 c. VAN AUSDALL TRANSMISSION Original Filed m. 24, 19656 Sheets-Sheet 6 United States Patent 3,546,951 TRANSMISSION Carl VanAusdall, Box 178, Bradenton, Fla. 33506 Original application Oct. 24,1965, Ser. No. 504,792, now

Patent No. 3,461,656, dated Aug. 19, 1969. Divided and this applicationAug. 11, 1969, Ser. No. 848,907

Int. Cl. A01d 35/24, 55/20; F16h 37/00 US. Cl. 74-1586 7 Claims ABSTRACTOF THE DISCLOSURE A transmission per se and in combination with anautomatic clutch. The transmission comprises a main drive shaft on whicha driving gear and jaw clutch member is rotatably mounted, first poweroutput means axially aligned therewith and including a reverse gear andjaw means for engaging the aforesaid jaw clutch and a slidable low gearon said output means; idler, cluster and reverse idler gears rotatablymounted off-center to said output means and main drive shaft, means foraxially shifting said member thereby engaging the transmission in highgear, such shifting means also slidable in a reverse direction wherebythe'reverse gear rotates the power output means in a direction oppositeto the main drift shaft; low gearing means axially slidable on saidoutput means and means for axially shifting such low gearing means toengage the cluster gear thereby providing for low gear transmission. Anoperable lever cooperates with each shifting means for providin'g adesired transmission engagement. There is further provided a powertake-off means coupled to the driving gear on the main shaft whereby,irrespective of low, high or reverse transmission gearing, engine speedis directly powered through such take-off means. The take-off meanscomprises a take-off shaft, a take-off gear freely rotatable on saidtake-off shaft and continuously meshed with the driving gear on the maindrive shaft, cooperative driving and driven jaw clutch members, thedriving clutch member rotatable with the take-off gear, the drivenclutch member being secured to the take-off shaft. Upon engagement ofsuch clutch members, the take-oif shaft rotates, and with such rotation,a pair of bevel gears rotates, one being secured to the takeolf shaftand the other secured to a driving means such as a shaft. An operablelevel actuates a shifting means for the driving clutch member, wherebythe clutch members engage.

This application is divisional application of my copending applicationfiled on Oct. 24, 1965, Ser. No. 504,792, and which issued on Aug. 19,1969 as US. Letters Patent No. 3,461,656.

This invention relates to a lawnmower apparatus and subcombinations ofelements therein, and in particular is related to a lawnmower machine inits entirety, a transmission adaptable for use in the machine and bywhich engine power is etficiently transmitted to a motive power driveshaft and ground wheels and to a reel mechanism, a combination of atransmission with an automatic clutch, a reel mechanism including novelbed plate knife and reel blade means therein, adjustable means forregulation of the reel blades and the bed knife means, and a swingingmechanism by which a proper amount of additional traction for the moweris obtained as a result of the added weight of the reel mechanism.

An object of this invention is to provide for a stable lawnmower machinethat will not upset, one which can maneuver in close quarters, one whichefiiciently moves and climbs across steep terrain or grades, one whichefficiently negotiates soft or uneven rough ground, and one that isreadily operated by a simple movement of the foot.

Another object of this invention is to provide for athree-point-to-ground suspension for the machine whereby it evenlyfollows the contour of the ground.

Another object of this invention is to provide for a trunnion-typemounting for the reel mechanism whereby the ground is not scalped uponmowing thereof.

Another object of this invention is to provide for a lawnmower machinecustomarily considered to be in the larger commercial class but whichnevertheless is suitable for homeowner use.

Another object of this invention is to provide for a safety constructionof a reel mechanism that eliminates the danger of ricochetin-g stones,sticks and the like, as well as preventing parts separated from themower from doing likewise.

Another object of this invention is to provide for a lawnmower of thereel type that cuts down and cuts up tall and thick grasses on plots ofground not previously prepared by mowing.

Another object of this invention is to provide for a mowin'g combinationof reel and knife that efficiently cuts grass and the like regardless ofits rank or massiveness.

Another object of this invention is to provide for a lawnmower thatincludes a safety feature whereby the lodgement of anything between theknife bed and the reel blades causes cessation of travel of thelawnmower, and,

removal of such lodging may be obtained without danger while the engineremains running.

Another object of this invention is to provide for an efiicient trunniontype mounting for a mower and other attachments.

Another object of this invention is to provide for anovel transmissionadaptable for use in my lawnmower.

Another object of this invention is to provide for a combination of aspiral reel blade having an angle, preferably between 30 and 50, to theplane of the ground at the point of contact with the bed plate knife anda bed plate knife whose leading or cutting edge is preformed at an angleto the plane of the ground so that the heel thereof cannot contact orpush grass, weeds, or the like downwardly out of the path of theoncoming reel blade before the cutting edge thereof is contacted by thereel blade, and thereby result in an eflicient cooperative relationship.

Another object of this invention is to provide for a mower having a reeland knife means that cut up what it cuts off.

Another object of this invention is to provide for a lawnmower thatstops instantly upon removal of the operators foot from the governorcontrol pedal connected to the machines engine.

Another object of this invention is to provide for addi tional andproper traction load for the ground tires by swinging the weight of themower or reel mechanism on such tires.

Another object of this invention is to provide for a power take-offmeans operatively connected to the gearing of the transmission.

Another object of this invention is to provide for an effectiveconnection between the power ta'ke-oif means and reel blades or otherattachments provided for the tractor or machine.

A still further object of this invention is to provide for a noveladjusting means for the efficient cooperation between the bed plateknife means and the reel blades.

Another object of this invention is to provide for continuance ofrotation of the reel blades even though the transmission is in neutral.

Another object of this invention is to provide for a novel tractormachine effectively suitable for mowing grass, removing snow, and otherlike tasks.

A further object of importance of this invention is to provide for acombination transmission and an automatic or centrifugal clutch whereby.firm non-slipping engagement of clutch to a drum attached to atransmission shaft is effected only upon attainment of a certain amountof torque or r.p.m. of an engine drive shaft, such torque or r.p.m.being operable on the clutch at higher values for rotation of the enginedrive shaft than at lower values thereof.

These and other objects and advantages will become apparent to thoseskilled in the art to which this invention pertains, upon a reading ofthe following description, appended claims therewith, and the drawingcomprising six sheets of figures taken in conjunction with thedescription and claims, and in which drawing:

.FIG. 1 is a front perspective view of my lawnmower apparatus embodyingthe hereinafter described invention;

FIG. 2 is a side perspective fragmentary view of mechanical linkage forsteering the machine;

FIG. 3 is a sectional plan view taken from the underside of a noveltransmission affording power to drive both the machine and a cuttingreel and blades therefor;

FIG. 4 is an exploded view, partly in section and partially broken away,of a portion of the transmission illustrated in FIG. 3;

FIG. 5 is an end view of a clutch mechanism adaptable for thetransmission illustrated in FIG. 3;

FIG. 6 is an elevational view, partially broken away, illustratingmechanical connections between manual motive means and the transmissionof FIG. 3, by which various gearing of the latter are engaged anddisengaged thereby;

FIG. 7 is a plan view, partially in section and partially broken away,of elements shown in FIG. 6;

FIG. 8 is an elevational view illustrating linkage between thetransmission of FIG. 3 and the reel and cutting blades of the mower;

FIG. 9 is an elevational view illustrating lever mechanism and othermeans by which the reel and housing therefor is upwardly pivotable froma ground-engaging position;

FIG. 10 is a side elevational view, partly broken away, of the reelhousing, illustrating a novel adjusting means for the mowers cuttingelements;

FIG. 11 is a plan view of FIG. 10, partly in section and partiallybroken away;

'FIG. 12 is a front view of a fragmentary portion 01 a bed plate memberwith knife means mounted thereon;

FIG. 13 is a side elevational view of the bed plate member with knifemeans mounted thereon;

FIG. 14 is a schematic diagram of a conventional bed plate knifeshearing edge;

FIG. 15 is a longitudinal full view of a reel and cutting bladesthereon;

FIG. 16 is an end view of FIG. 15;

FIG. 17 is an end view of a modified reel; and

FIG. 18 is a fragmentary full view of reel axle and blades and showing amodified construction at the ends thereof.

'Referring now to the figures in which reference characters correspondto like characters in the following description, character 20 (FIG. 1)illustrates generally the lawnmower apparatus. Machine 20 includes aconventional piston-type engine 21 suitably fixed centrally of and atthe front end of a frame 22 suitably mounted upon a set of three freelyrotating rubber or balloon tires 24, the front two tires being spacedlymounted on a transversely disposed axle (FIGS. 1, 8), and by which threetires mower 20 is displaced across ground. The fixing and mounting ofengine to frame and axle to wheels may be effected in customary mannerknown in the power mower industry, however, it should be observed thatengine 21 is vertically disposed centrally above axle 25 on which thetwo front tires 24 are rotatably mounted.

TRANSMISSION AND CLUTCH Engine 21 is so oriented that its rotating crankshaft (not shown) extends longitudinally rearwardly of mower 4 20whereby a clutch member 28 (FIG. 5) fixedly secured to such crankshaftis disposed in engageable position with a clutch drum 29 of an automatictransmission 30 housed at the rear of engine housing 31 (FIGS. 3, 8).Clutch member 28 is of the automatic type, such as the one disclosed inmy patent for a centrifugal clutch, US. Pat. No. 2,696,282, issued Dec.7, 1954. Clutch 28 is preferably mounted to the engine crankshaft in themanner disclosed in such patent.

Clutch drum 29 (FIG. 3) is provided with a central aperture 33 thesurrounding defining portion of which is suitably secured to a clutchadaptor 34 slideably mounted onto a main drive (M.D.) gearing shaft 35.A Woodniff key 36 is provided between shaft and adaptor 34 to preventrelative rotation between drum 29 and shaft 35. Both adaptor 34 and drum29 are held axially stationary upon M.D. gearing shaft 35 between ashaft snap ring 37 engaging a well 3 8 recessed in adaptor 34 and a ballbearing housing 40 securely held in an opening -41 provided in a castportion 42 projecting interiorly of metal transmission housing 30a. Twosuch ball bearing housings 40 are preferred, as shown in FIG. 3, eachflush with and bearing against the other in opening 41, and held thereinby a suitable pair of snap rings 43 mounted in annular grooves in ballbearing housing 40, and which rings 43 seat against the sides ofperipheral recesses 44 formed in cast portion 42 about opening 41.Consequently, when clutch drum 29 is engaged by clutch 28 (FIG. 5), MD.gearing shaft 35 rotates in the bearings contained in bearing housings40, with the speed of rotation of the crankshaft of engine 21.

Integrally formed on the other end of MD. gearing shaft 35 is a maindrive (M.D.) gear 45 (FIGS. 3, 4) engaging Other gears in transmission30 to be described. M.D. gear 45 is preferably spaced from bearinghousing 40 by means of a cylindrical shoulder 46 (FIG. 4). Formed as anintegral part to shaft 35 is a driving clutch member 47 (FIGS. 3, 4)provided for transmitting to wheel axle 25 to engine speed of machine20. A bore 48 is concentrically provided in member 47 and MD. gear 45for disposition of one end of a first power output (f.p.o.) shaft 49. Abushing 50 is mounted in bore 48 about shaft 49 to prevent frictionbetween such shaft 49 and driving clutch member 47. A combination drivenclutch and gear member 51 is slideably mounted on f.p.o. shaft 49 and isprevented from rotating about such shaft 49 by means of a square-shapedelongated key member 52 axially shiftlessly disposed in its peripheralsurface and parallel to its axis. A lever shifting fork 53 (FIGS. 3, 6,7) is slip-fittably coupled to a recessed central portion (FIGS. 3, 6)in combination member 51. Shifting of fork 53 to-and-fro along the axiallength of shaft 49 provides for engagement and disengagement betweendriven and driving members 51 and 47. In engagement, f.p.o. shaft 49rotates with the speed of rotation of MD. gear shaft 35, and hereafterin this continuing description, such engagement is defined as high gear.

The specific structures of driven and driving members 51 and 47 andcomprising various notches or dog teeth on said members that areinterrelated with each other when both members engage or mesh with eachother in gear, are generally known in the art, and a suitablecombination thereof may be used to provide for unitary rotation ofshafts 35, 49.

F.p.0. shaft 49 is supported at its other end in a pair of bearinghousings 55, similar in nature to bearing housings 40, as it projectsthrough the rear wall of transmission housing 30a (FIG. 3). A coverplate 57 is provided to cooperate with cast portion 58 for supportingsuch housings 55, and in addition, cover plate 57 seals off the interiorof transmission 30. The free end of shaft 49 projecting through coverplate 57 is adapted for mounting a sprocket wheel 60 (shown in phantomin FIG. 3; FIG. 8) that is fixedly keyed at 61 on shaft 49. As shown inFIG. 8, a link chain 62 connects such wheel 60 and shaft 49 to a similarsprocket fixedly mounted on a power transmission (p.t.) shaft mounted ina housing 63 disposed below transmission 30 and engine housing 31.Housing 63 extends centrally of and longitudinally forwardly in anunderslung position of apparatus and is suitably connected to axlehousing containing conventional differential axle elements (not shown)by which each front tire 24 is capable of rotating together orindependently of the other front tire 24 in a customary manner. Thus, apower train connects transmission 30 with axle for providing motivepower for machine 20.

A second driven member or gear 65 is provided for a low gearing ratiobetween engine speed and ground speed of lawnmower 20. Gear 65 isslideably mounted on f.p.o. shaft 49 adjacent to but spaced from bearinghousings 55, and is likewise keyed by key 52 to shaft 49. A second levershifter fork 66 (FIGS. 3, 6, 7) is provided to slideable axially actuatedriven gear member 65 along shaft 49 whereby a low gearing ratio betweenthe crank shaft (not shown) of engine 21 and f.p.o. shaft 49 can beeffected. Shifter fork 66 is cooperatively received about a reducedcentral portion of collar 67 integrally formed with gear member 65,whereby the latter is capable of being slideable on shaft 49.

As driven member 65 is axially displaced forwardly along shaft 49 bymeans of fork 66, its teeth engage an idler cluster gear 70 rotatablymounted upon a cluster gear shaft 71 spacedly positioned from butprovided on center with and parallel to f.p.o. shaft 49 (FIGS. 3, 6).Cluster gear shaft 71 is pinned against rotation, as at 72, in cast 58of transmission housing a that supports it. Idler cluster gear 70 isformed integrally upon one end of a sleeve 73 freely rotatable uponcluster gear shaft 71. At the other end of sleeve 73, an idler gear 74is integrally formed and positioned to continuously mesh with main drivegear 45. A pair of bushings 75, 76 is provided for frictionless rotationof sleeve 73 on cluster gear shaft 71, and a pair of cluster gearspacers 78, 79 is mounted on cluster gear shaft 71 each at an oppositeend of sleeve 73, adjacent bushings 75, 76, respectively, and contiguousto cast portions 58, 42, respectively, of transmission housing 30a, inorder to provide for proper spacing and cooperative association of idlergears 70 and 74 with gears 65 and 45, respectively.

Consequently, to effect a low gearing for forward motion of lawnmower20, shifter fork 66 is axially advanced forwardly along f.p.o. shaft 49so that gear 65 meshes with idler cluster gear 70 with which idler gear74 continuously rotates. Idler gear 74, of course, rotates whenever M.D.gear rotates. Hereafter in this continuing description, such low gearingwill be described as low gear.

It should be noted that combination member 51 and members 65, 67although freely axially slideable on f.p.o. shaft 49, are neverthelesslimited to specific axial movements dictated by the limits of axialmovement of their respective lever shifter forks 53, 66 thatrespectively cooperate with them.

Reverse or rearward motion of machine 20 is provided by cooperativeaction of shifter fork 53, MD. gear 45, idler cluster gears 74, 70 and asliding gear 80 included in combination member on f.p.o. shaft 49, and aseries of gears mounted on a reversing shaft 81 provided oflf center toand in spaced parallel relationship to shafts 49 and 71, preferablydisposed below shafts 49, 71 as shown in FIG. 6. The ends of reversingshaft 81 are mounted in cast portions of transmission housing 30a, itbeing pinned (not shown) to cast portion 58. A collar 82 is mounted andpinned (not shown) to shaft 81 to prevent axial movement and maintainalignment of an idler gear 83 mounted on a bushing (not shown) onreversing shaft 81. Idler gear 83 rotates as a consequence ofcontinuously meshing with idler cluster gear 70 on sleeve 73 (FIGS. 3,6) rotating about cluster gear shaft 71. Reverse idler gear 83 mesheswith sliding gear 80 on f.p.o. shaft 49 upon the latters axial actuationby shifter fork 53. Sliding gear 80 meshes therewith by rearward axialmovement of combination member 51 on f.p.o. shaft 49. Such meshingeffects an opposite rotation of f.p.o. shaft 49 to that of MD. gearshaft 35 and the crankshaft of engine 21 of the lawnmower. Consequently,the mechanical power transmitted through axle 25 to tires 24 is reversedin direction and mobile machine 20 moves rearwardly. Hereafter in thiscontinuing description, such reverse gearing will be described asreverse.

Each of shifter lever forks 53, 66 is supported (FIG. 7) on one of apair of spaced parallel arms 86, 87 respectively, that is slidable inbores 88a, 88b, and 89a, 89b, respectively. Such bores are horizontallydrilled in a preferably upper half casting 90 (FIGS. 6, 7) verticallydisposed above and suitably secured to the lower half of transmissionhousing 30a by threaded bolts 91 the crosssections of which are shown inFIG. 3. Shifter fork 53 comprises a cylindrical hollow sleeve 92 (FIG.7) pinned to arm 86, as at 93, and having a pair of depending spacedtines 94 (FIG. 6) that cooperate with combination member 51, asprevious-1y described. Included in sleeve 92 is an axially-disposedcircumferential recess 95 (FIG. 7) into which an end 96 (FIG. 6) of amanuallyoperable pivotal lever 97 is receivable. Recess 95 is disposedalong the length of arm 86 in a manner that is in direct oppositeconfrontation to a like recess 98 included in arm 87 upon which shifterfork 66 is mounted. Shifter fork 66 comprises a cylindrical hollowsleeve 99 pinned to arm 87, as at 100 in FIG. 7, and having a pair ofspaced depending tines 101 integrally formed therewith and dependingtherefrom to cooperate with driven clutch member 65, as previouslydescribed.

End 96 of lever 97 is juxtapositioned between recesses 95, 98 forcooperative action with each of arms 86, 87 as will be hereinafterdescribed.

Each arm 86, 87 is slidable in its respective supporting bores 88a, 88band 89a, 8917 (FIG. 7) disposed in casting 90 so that shifter forks 53,66 axially displace along f.p.o. shaft 49 and thereby actuate thegearing mechanisms heretofore described. All of such supporting boresare sufliciently deep to provide for the space necessary forreciprocation of arms 86, 87 during gearing changes effected byactuation of transmission 30.

In order to ensure the gear meshing desired by their respective shifterforks 53, 66, a detent means 105 (FIG. 7) is provided to cooperate witheach of arms 86, 87. By such cooperation each arm 86, 87 is reciprocateda predetermined distance to accomplish the aforesaid described gearingratios in low, high and reverse gears. For arm 86, detent means 105comprises a detent ball 105a biased by a compressed spring 1051).Elements 105a, 1051) are seated in a bore 108 disposed in casting 90 andperpendicularly bisecting supporting bores 88a, 89a. Similarly for arm87, detent means 105 comprises a detent ball 105a biased by a compressedspring 105d with both such elements also seated in bore 108 in the samemanner as elements 105a, 10511.

Each of arms 86, 87 includes a series of notches or grooves that engagea detent means 105 to axially position the arm, and consequently,shifter forks 53, 66 into high or low gears, and reverse gear,respectively. Arm 86 is provided with an annular groove 110 that itscorresponding detent means 105a, 105b engages to maintain shifter fork53 in neutral position (transmission out of gear, i.e.). Likewise, arm87 is provided with an annular groove 111 that its corresponding detentmeans 105c, 105d engages to maintain shifter fork 66 in neutralposition. The gearing of transmission 30 is in neither of the twoforward gears or in reverse gear.

It may be noted here (FIG. 7) that recesses 95, 98 in sleeve 92 and arm87, respectively, directly confront each other when transmission 30 isin neutral, and that it is end 96 of lever 97 that projects downwardlyto be juxtapositioned between such recesses that causes reciprocation ofone or the other of arms 86, 87. It is this confronting 7 positioning ofrecesses 95, 98 that places transmission 30 in a neutral position, withno power being transmitted to axle 25 of machine 20 from the crank shaftof engine 21.

Pivoting of lever 97 places the transmission gearing into one of threepositions from neutral position; forward gear, reverse gear, or lowergear; each of such gearing correspondingly propels apparatus 20forwardly at a high speed, rearwardly, r forwardly at a relatively lowspeed.

The pivoting of lever 97 requisite to axially displace either one ofshifter forks 53, 66 is provided as follows. Mounted along the length oflever 97 is a spherical element or ball 115 (FIG. 6). Ball 115 isdisposed within a hollow cone cast portion 116 of the upper transmissionhousing half 90, such portion 116 being generally aligned with thelength of lever 97. Spherical element 115 is biased upwardly against anopening 117 in the apex of such portion 116 by means of a leversupporting conical helical spring 118 under compression. Spring 118 isseated upon a plurality of angular projections or lips 119 situated nearthe base of cone portion 116, and has its smaller helical end engagingspherical element 115. Spherical element 115 is provided with adiametrical bore that is adapted to register with a like bore in lever97. These bores seat a levelly aligned pin 120 that maintains the properdisposition of lever 97, more particularly its end 96, in relation toarms 86, 87. Also formed in ball 115 is a vertically aligned slot 125 inwhich a headed rivet 127 is disposed. The end 128 of rivet 127 is seatedin a hole in cone casting 116 so that lever 97 and its end 96 does notrotate about its axis whereby end 96 would not consistently properlyengage recesses 95, 98 in all instances of use.

Thus, it should now be apparent that by manipulating lever 97 manuallyby its knob 126, lever end 96 cooperatively engages either recess 95, 98to the exclusion of the other so that only the arm 86 or 87corresponding to its engaged recess 95 or 98 is reciprocated. However,the juxtaposition of lever end 96 between recesses 95, 98 provides forphysical possibility of mutually engaging cooperation with both recesses95, 98.

To ensure exclusionary reciprocation of one arm to the other, means areprovided in bore 108 to prevent either of such arms '86, 87 fromreciprocating while the other is reciprocating. As shown in FIG. 7 alocking pin or detent 130 is slidably seated in the portion of the bore108 disposed between arms 86, 87. Its total length is slightly greaterthan the shortest distance between bores 88a and 89a. Each of therounded ends of detent 130 is adapted to engage one or the other ofcorrespondingly rounded annular grooves 110, 111 in arms 86, 87respectively. Reciprocation by lever end 96 of one or the other of arms86, 87 from out of its neutral position causes detent 130 to move intocooperative engagement with the annular groove of the other arm therebypreventing such latter arm to reciprocate. Therefore, no damage ispossible to the gearing mechanism of transmission 30 by manipulation oflever 97.

The extent of reciprocation of either arm 86, 87 is limited bycooperative action of detent notches defined in each arm and itscorresponding detent means 105. As each arm 86 or 87 is reciprocatedfrom out of its neutral position by means of its corresponding shifterfork, another position therefor is established by the locking of adetent notch with one of detent means 105. Notch 132 is defined in arm86 on one side of annular groove 110 and notch 133 is defined in arm 86on the other side of annular groove 110. Groove 134 is defined in arm 87as shown in FIG. 7. The spacing apart of each of detent notches 132, 133and 134 from their corresponding annular grooves 110, 111 on theirrespective arms 86, 87 is correlated to the particular gearing (high,reverse, or low) to be accomplished in transmission 30. The spacing ofdetent notch 132 from annular groove 110 is correlated to the movementof shifter fork 53 from neutral position to a position at which drivingmember 47 and driven member 51 are engaged (high gear). The spacing ofdetent notch 133 from annular groove is correlated to the movement ofshifter fork 53 in an opposite direction for proper meshing of gear 80with reversing gear 83 (reverse gear). And the spacing of detent notch134 from annular groove 111 is correlated to the movement of shifterfork 66 from neutral position to a position at which member 67 hassufiiciently advanced for proper meshing of gearing 65 with cluster gear70 (low gear).

POWER FOR REEL Transmission 30 also includes an efficient gearingmechanism to rotate lawnmower reel blades from the engine speed in anyof the forward, stopped, or rearward motions of the apparatus 20-.

As shown in FIGS. 3, 6, a second power output (s.p.o.) means is providedin cooperative relationship with M.D. gearing shaft means 35. Means 140comprises a take-off gear 142 freely rotatably mounted on an s.p.o.shaft 143 journaled in a pair of spaced suitable bearings 145, 146, adriven member 148 securely fixed to shaft 143 and adapted for engagementwith a driving member 150 integrally formed with gear 142, a pair ofbevel gears 151, 152, the one gear 151 being mounted upon and keyed asat 154 with shaft 143, the other bevel gear 152 in meshing arrangementat 90 with bevel gear 151, and a journaled driving shaft 155 adapted forconnection to a reel mechanism for machine 20. Driving shaft 155 ispreferably integrally formed, or is otherwise suitably coupled, to bevelgear 152.

Take-off gear 142 is in continuous mesh with M.D. gear 45, therebycontinually rotating when engine 21 is operating and automatic clutch 28is engaged with drum 29. Gear 142 is free of frictional and fixedengagement with shaft 143 by means of a cylindrical bushing (not shown)separating them, and which bushing also effectively serves to freesecond driving member 150 also from shaft 143. The second driven member148, keyed as at 157 to shaft 143 for unitary rotation therewith, isnevertheless axially displaceable along shaft 143 for engagement withdriving member 150 by means of a shifter fork 159.

Shifter fork 159 is similar in make to shifter fork 66 and comprises acylindrical hollow sleeve 160 having a pair of spaced tines 161depending therefrom (FIGS. 7, 6). Sleeve 160 fits a reciprocable arm 162on center line with, displaced from, and parallel to the axes of arms86, 87 (FIG. 6), and is pinned thereon as at 164 in FIG. 7. Thedepending pair of tines 161 embraces a reduced central portion of drivenmember 148 so that the latter axially displaces along shaft 143 uponreciprocation of arm 162. Arm 162 is supported in bores 166a, 16Gbdisposed in cast portion 90 of transmission housing 30a, such boresbeing sufficiently deep to provide space for reciprocation thereof. Asshifter fork 159 is actuated, driven member 148 engages or disengagesfrom driving member 150, as the case may be, thereby locking orunlocking such members. Driving and driven members 150, 148 are similarin nature to members 51, 47, and are well known in the art.

To actuate shifter fork 159, arm 162 is reciprocated by means of asecond lever 168 pivotable about a fulcrum in a second hollow cone castportion 169 of the transmission housing upper half 90. Cone portion 169is preferably in parallel relationship to cone portion 116. Such fulcrumcomprises a rod 170 horizontally supported in cone casting 169 as shownin FIG. 6. Rod 170 extends diametrically through lever 168 in a levelmanner and perpendicularly to the axis of arm 162. A tang (not shown) isintegrally formed at the base of lever 168 and is accommodated in aperipheral groove 171 (FIG. 7) of arm 162, thereby providing for theconnection by which arm 162 is reciprocated by pivotal movement of lever168.

The extent of reciprocation of arm 162 is controlled by a detent means173 (FIG. 6) that registers in one or the other of a pair of detentnotches 174 (FIGS. 6, 7)

provided in arm 162 (FIGS. 6, 7). Detent means 173 is disposed in a holeor bore drilled in cast portion 90, and comprises a ball and spring thatfunction in a similar manner to that of detent means 105 used inconnection with arms 86, 87. The ball of detent means 173 is biased inone or the other of detent notches 174 formed in arm 162. Consequently,as shifter fork 159 axially moves as a result of lever 168 pivotingabout its fulcrum 170, detent means 173 cooperates with one or the otherof detent notches 174 thereby controlling the positioning of arm 162.The spacing between the two notches 174 on arm 162 is correlated to thedistance required for movement of driven member 148 axially along shaft143 to properly and fully engage and disengage driving member 150.

A cylindrical spacer 176 (FIG. 3) is mounted about shaft 143 between awasher 177 adjacent bearing 145 and bevel gear 151. Further, a washer178 separates bevel gear 151 from driving gear 142. A bushing (notshown) is mounted in gear 142 and adapted to engage a shoulder (notshown) on shaft 143 to prevent axial movement of gear 142. Thus, drivinggear 142 is maintained in proper alignment and meshing engagement withM.D. shaft gear 45. Spacer 176 also functions to maintain properrelative positioning of bevel gear 151 to its co-acting bevel gear 152.

The mounting of these parts as shown provides for the facileregistration of one or the other of detent grooves 174 in arm 162 withdetent means 173, and thereby avoids unalignment of the heretoforedescribed elements of s.p.o. means 140 that could otherwise makeunworkable transmission 30 or damage same.

With driven member 148 locked onto driving member 150, meshing bevelgears 151, 152 rotate, with the consequent rotation of power take-offshaft 155. Shaft 155 is journaled in a pair of suitable bearings 180,181 (FIG. 3) housed in an outlet tubing 182, preferably horizontallydisposed, provided in transmission housing 30a. It should be observedfrom FIGS. 6 and 3 that an advantage of a plurality of dispositions fortubing 182 arises, relative to bevel gear 151. For example, tubing 182and bevel gear 152 may be swung through an angle or any fractionabledegree thereof so that power take-off shaft 155 may be directed asdesired. In FIG. 6, phantom lines 182a represent any one of suchplurality of positions for shaft 155, for it is clear from FIG. 6 thatbevel gear 152 may be readily swung about bevel gear 151 and stillremain in cooperative relationship therewith. l

It should now be apparent that apparatus may be propelled without powerbeing transmitted to its reel mechanism, simply by not actuating lever168 whereby members 148, 150 would engage and lock. Furthermore, powerto the reel mechanism can be transmitted to the reel and cutting bladesthereof independently of motion or non-motion of machine 20, as a resultof power being transmitted to s.p.o. means 140 separate and apart frompower transmitted to f.p.o. shaft 49.

LINKAGE MECHANISM BETWEEN TRANSMISSION AND REEL FIG. 8 illustrateslinkage mechanism 183 by which power at take-off shaft 155 istransmitted to a reel mechanism 185 mounted on apparatus 20. A firstlink chain 186 is mounted upon a pair of sprocket wheels 187, 188, wheel187 (FIGS. 8, 3) being fixedly mounted to s.p.o. shaft 155 and wheel 188being disposed directly forward of wheel 187 and bearingly mounted atthe inner end of a laterally disposed axle housing 190 whose inner endis secured to the side of engine housing 31. The inner end of axlehousing 190 may also be fastened to an angle-iron element or the likeconstituting part of frame 22. A second link chain 192 is mounted upon asecond set of sprocket wheels 194, 195, wheel 194 being bearinglymounted adjacent the outer end of laterally disposed axle housing 190and wheel 195 being bearingly mounted adjacent the inner end of a secondlaterally disposed axle housing 197. Axle housing 197 is disposedforwardly and preferably at an elevated height with respect to axlehousing 190, and is secured to a cross-bar 3-64 (FIGS. 1, 9) securelyfastened, as at 366 in FIGS. 1, 9, to respective triangular elements200a, 200b, of a pair of bracket members 200 the lower ends of which areswivelly supported exteriorly to a reel housing 202. A third link chain206 is rotatably coupled about a third set of sprocket wheels 208, 209,wheel 208 being bearingly mounted on the outer end of housing 197 andfreely projecting through one element 200 (FIG. 1) and wheel 209 beingfixedly mounted on an extension 222 of a reel axle of reel mechanism185. It should be understood from FIG. 8 that each link chain, 186, 192,206 is longitudinally arranged with respect to the length of machine 20,and are generally parallel with each other.

It should now be apparent that the rotation of s.p.o. shaft provides foractuation of the variously linked sprocket wheels and chains justdescribed so that power directly from the engine speed proper istransmitted to reel mechanism 185. Various speeds of rotation of thecutting reel blades in reel mechanism may be obtained by varying theratios of the described sprockets. Also, low gear does not preventeffective mowing and cutting up of tall and thick grass, since the speedof the reel blades is consistent with the engine speed directly off ofshaft 35 although the ground speed of machine 20' is small in vieW oflow gear.

HOUSING Asshown in FIGS. 1, 9, 10 and 11, a reel housing 202 includes acast or molded pair of vertical walls 227, 228 securely connectedtogether such as by bolts through a rigid angle iron 229 edged laterallyalong the forward terminus of a top wall 230 extending transverselyacross the width of the reel and generally of machine 20 (FIG. 1) and bybolts 232 through top wall 230 adjacent the rear of wall 227, 228. Eachvertical wall 227, 228 is provided with an elevated forwardly projectingextension 234, 236 respectively, for mounting of a ground caster wheel238 therebelow and adapted to freely rotate to any degree or directionas it progresses revolvingly across ground as machine 20 is propelled.Each caster wheel 238 is suitably rotatably mounted in a forked member240 having a rod 242 integrally formed at its apex and disposed andbearingly mounted in a sleeve 244, 246 correspondingly formed ofextensions 234, 236, as shown in FIGS. 1, l0.

Caster wheels 238 are adapted to cooperate with a ground roller 250(FIGS. 10, 11) transversely disposed at the rear and bottom of housing202 and which is adapted to maintain contact with ground surface. Groundroller 250 cooperates with caster wheels 238 to maintain support of reelhousing 223.

Ground roller 250 is rotatably mounted between a pair of verticallydisposed elongated bracket members 252 the height of each of which beingadjustably secured to an exterior surface of each of the vertical walls227, 228 adjacent their respective rear terminus edges. Cast or moldedin each of walls 227, 228 is a pair of spaced vertically aligned flanges254 between which a bar bracket 252 is disposed. Each bracket 252includes a series of apertures any one of which is adapted to registerwith one of a plurality of holes in its corresponding wall 227, 228,whereby a threaded bolt or bolts 255 secure bracket 252 and roller 250to housing 202. Such registration and securing together by bolts 255provide an adjustability for the height of roller 250 whereby housing202 is adjustably lowered or raised in relation to the ground contactmade by caster wheels 238. Consequently, the plane of cutting grass andthe like by means of the cooperative action between reel blades and bedplate knife means hereinafter described, is adjustable in height overthe ground surface, thereby obtaining a desired cutting height for grassor the like.

A preferred bearing means 2'60 for each end of ground roller 250,whereby efficient lubrication and revolution of roller 250 across groundis achieved and maintained, is

shown in FIG. 11. A nipple 261 is provided at the egress point of aconduit 263 in a bearing support 264 whereby lubrication is effected andthrust into spaces provided on each side of bearings 266 mounted inbearing housing 267. A radially extending conduit 268 carrieslubrication to space 269 on one side of bearings 266 and conduit 263carries lubrication to space 271 on the other side of bearings 266through the center of the bearings. Nipple 261 conveniently projects outof each bracket 252 for lubrication purposes.

BED PLATE KNIFE MEANSSTRUCTURE A bed plate knife means 275 (FIG. thatcooperates with rotating blades of reel mechanism 185 is mountedtransversely across the bottom of reel housing 202. Means 275 comprisesa molded or cast, generally elongated, member 276 having an upwardlyfacing curved surface 277 across which cut grass is swept up along arear wall (not shown) of housing 202 and over roller 250, and a knifemeans 279 including a shearing lip or edge 280. Curved surface 277extends across the interior width of reel housing 223.

Knife means 279 is formed from a suitably tempered metal member revetedco-extensively along and to the fiat bottom of the portion of member 276constituting the base of curved surface 277, as at 282 shown in FIGS.12, 13.

Knife means 279 comprises a shearing element, edge or lip 280 thatpreferably includes a material thickness 2801 to rely upon forsharpening purposes in addition to providing for a shearing surface. Lip280 projects upwardly and at an angle with respect to the plane of theground or the riveted portion of member 279. A relief 2801' is formed inthe heel of lip 280 below the the shearing surface or plane of actionthereof. Consequently, the shearing or cutting edge of lip 280 leads asknife means 279 advances across ground. It is important to note here theadvantage obtained by such relief 280r preformed in knife means 279.FIG. 14 shows a crosssectional elevation of a standard or conventionalbed plate knife means 285 comprising a vertically aligned edge 285:;having no relief in its heel 28512. Consequently, as standard bed plateknife means 285 is thrust forwardly across ground, grass stalks and thelike are shoved forwardly and downwardly by heel 285/z, out of the pathof an oncoming revolving reel blade, instead of remaining upright or intheir otherwise natural growing state for cutting off at a uniform levelat the plane of shearing that occurs 285s. What occurs is the sweepingor shoving of uncut grass along the length of edge 2852 by heel 28511 atthe same instant of cooperation between knife and reel cutting bladeinstead of a reel blade cutting such grass that is engaged by the knifeat the instant of cooperation between blade and knife (at 285s). Arelatively choppy, uneven or wavy cut grass apron or area is achievedwith use of such a standard knife means 285, whereas my knife means 279does not brush or sweep aside grass prior to or at the instant ofcontact between the reel blade and the shearing plane at lip 280. Itprovides for an immediate and more uniform cutting, an unexpected resultby the inclusion of a preformed bed plate knife having a relieved heel280).

BED PLATE KNIFE MEANS-MOUNTING Each of the lateral ends of bed platemember 276 is provided with a horizontally disposed fiat extension 290one of which is shown in FIGS. 10, 11, and 12. Extensions 290respectively extend to the outside of each of their correspondingvertical walls 227, 228 of housing 223. Each flat extension 290 isprovided with a pair of spaced threaded holes 292 vertically alignedtherein and registrable with a pair of hollow bores 294 included in anovel bracket member 295 (shown in FIGS. 10 and 11) adapted to beattached to a corresponding vertical wall 227, 228. A threaded bolt 296is inserted in each bore 294 over a washer 297 seated on the top 12 ofeach bore 294 and is threaded tightly to corresponding threaded holes292 in the flat extension 290.

ADJUSTABILITY OF BRACKET MEMBER AND BED PLATE KNIFE MEANS Each ofbracket members 295 mounted to its respective vertical wall 227, 228comprises an element adapted to pivot at its rear end portion 310, atwhich a fulcrum is formed by means of a bolt 312 through such endportion 310, the bolt 312 retaining member 295 to its respective wall227, 228, and having a second end 314 disposed forwardly of bores 294.An elongated slot 316 is defined in end portion 314 in a generallyvertical manner so that it reciprocates upon a stationary bolt 318-threaded into its associated wall 227, 1228. By loosening bolts 312 and318 that extend through member 295 and into each wall 227, 228, member295 is pivotable about bolt 312 to the extent of the length of slot 316.Consequently, bed plate knife means 275 that is secured to bracketmember 295 is displaceable away from or towards the reel blades of reelmechanism 185.

Means are provided for adjusting and controlling the spacialrelationship between bed plate knife means 275 and the reel blades inorder to maintain elficient shearing action and to utilize the thicknessof material 280t, and for controlling the extent of pivotal movement ofbracket means 275. Disposed along the length of each means 275intermediate of the pair of bores 294 and slot 316 is a portionincluding a vertically aligned screw threaded bore 320 adapted to bedisposed over a lug or portion 322 laterally engaging a correspondingwall 227, 228. Each lug 322 is preferably cast in each wall 227, 228. Athreaded screw 324 is seated in bore 320 with its free end registeringupon a lug 322. Rotation of the pair of bolts 324 one way or the otheragainst the threads of bore 320, after loosening of bolts 312 and 318and a lock nut 326 for each bolt 324, arcuately raises or lowers bedplate knife means 275, and consequently shearing edge 280, as a resultof the pivotal action of bracket members 295 that fixedly carry flatextensions 290. It is clear from the illustrated figures that the arc ofknife means 275 crosses the arc of rotation of the reel blades as lawnmower 20 advances across ground.

REEL AND BLADES THEREON As illustrated by FIGS. 15-18, reel mechanism185. is provided wiih a plurality of rotating cutting blades 330connected to an axle 332 bearingly mounted as at 331 (FIG. 11) tovertical side walls 227, 228. The embodiment of the inventioncontemplates two forms of mode of operation for reel blades. As shown inFIGS. 15, 16, a pair of uniformly opposed blades 330 are helicallywound, each through an angle of about the length of axle 332 and withinthe confines of walls 227, 228. These blades 330 are spaced from axle332 a proper radial distance in order to effectuate an efficientshearing action with bed plate knife means 275 heretofore described.Such spacing is provided by spokes 334 perpendicularly disposed to axle332, pairs of which oppose each other on opposite sides of axle 332. Aplurality of such pairs of spokes 334 are angularly oriented about reelaxle 332 in order to provide for the helical configuration for eachblade 330. A strong weld between axle 332 and each spoke 334, and eachspoke 334 with its associated blade 330, is preferably sought inconnecting such elements together.

FIG. 17 illustrates the use of a four-bladed reel having four cuttingblades 336 uniformly helically or spirally wound about an axle 338. Eachblade 336 is also helically wound through 180 about the length of axle338 and within the confines of walls 227, 228. Each blade 336 isspacedly supported from axle 338 by a plurality of spaced angularlyoriented spider members 340 each of which incorporates four spokes 342one for each blade 336. Each spider member 340 includes a hub portion 13344 about a central orifice into which axle 338 is received, and, ofcourse, welding of axle to spider and spider to blade is the preferredmanner of securing these connections together.

It should be understood that FIG. 17 should not be interpreted asshowing that each blade 336 spirals through only 90. Viewing blades 336of FIG. 17 in a clockwise manner, each blade winds spirally behind eachsuccessive blade 336 that is phased at its first and 90 in advance ofthe first end of the preceding spirally wound blade 336 in FIG. 17, suchthat the spiral winding of each blade 336 after uniformly windingthroughout its length effects a 180 angle at its last end.

FIG. 18 illustrates a modification of a spoke or spider connection forthe blades and axle of reel mechanism 185. It is preferred that thelateral ends 350 of each of the blades are immediately juxtapositionedto the interior face of its corresponding vertical wall 227, 228, toachieve as wide a path of cutting as possible. Spokes or spider members352 that are adjacent ends 350 are slanted inwardly therefrom to besecured to an axle 354, in order to provide for sufficient length ofaxle 354 at its respective ends to be suitably mounted on its journalledbearings that are contained generally within the thickness of walls 227,228.

Only one point of cooperative action at any instance in time is realizedbetween shearing edge 280 and the reel blades 330 exemplified in FIGS.15, 16, and at any instance of time for shearing edge 280 and the reelblades 336 exemplified in FIG. 17, only two points of such cooperationare realized. In the latter case, the first point of cooperation lies ona first blade 336 that is rotating into knife means 275, and the secondsuch point is to be found on the immediately following rotating blade336 that is phased 90 behind the first blade 3.3-6. The advantage inthis design of blades maintains a constant pull on the sprocket chainsthat transmit power from transmission 30 t axles 332, 338, and therebyeliminates vibration that would otherwise develop in such axles and betransmitted in return to the sprocket chains. An irregular pullingeffect on such chains is otherwise set-up were three or five bladedreels introduced for cooperative action with bed plate knife means 275,with consequent damaging effects occurring as a result of uncontrollablevibration.

As shown in FIG. at the point of cooperative relationship between eachblade 336 (or 330) secured to its spiders or spokes and the shearingsurface of lip 280 of bed plate knife means 275, the mounting of eachsuch blade as it spirally winds on its reel provides for the plane ofthe reel blade to form an angle relative to the ground as it sweeps overlip 280 and sweeps through with rotation of its reel. This angle liespreferably between 30 and 50 the spread of which includes the mosteffective cutting angle for each blade 336' (330) as it co-acts withupwardly projecting lip or edge 280.

SWINGING MECHANISM FOR TRACTION AND FOR AVERSION OF DAMAGE TO REELMECHA- NISM FIGS. 9 and 1 illustrate apparatus by which additionaltraction is obtained in optionally varying degrees for machine 20. .Inuse over rough or muddy terrain, additional traction may be required oris otherwise desirable. Its purpose also includes aversion of looseobjects, or grounded obstacles, or the like that could damage reelmechanism 185. Means 360 is provided for reel mechanism 185 and itshousing 202 whereby same are wholly lifted in a swinging fashionupwardly from ground engagement. The combined weights of mechanism 185,housing 202, and of the operator of vehicle 20 by his efforts to swingsuch mechanisms are advantageously utilized to gain advantageoustraction on front tires 24.

Means 360 is generally pivotally mounted on frame 22 and extendsforwardly of engine housing 21, and is actuable by the operator of thevehicle while sitting at 442 (FIG. 1). Each of a pair of raising levers361 are pivotally attached at its rear end to a longitudinal framemember 22 located below and to each side of engine housing 21. The otherends of each of raising levers 361 are secured, as by welding, to across-bar 364 levelly traversing machine 20 between engine housing 21and reel housing 202. Each of the pair of connecting molded elongatedbracket members 200 include a triangularly shaped portion 200a, 20012that is suitably and securely mounted or fastened, such as at 366 shownin FIGS. 1, 9, to a corresponding end or flat bracket member 365 ofcross-bar 364. Bracket members 200 are disposed in parallel spacedrelationship with each other and both slant downwardly and forwardlyalong the exterior faces of vertical walls 227, 228 to support suchwalls on circular steel inserts 368 (one of which is shown in FIG. 11)integrally mounted in members 200. Each bearing 331 (FIG. 11) whichcarries the reel axle is mounted in its corresponding steel insert 368so that the mower itself, with housing 202, floats in members 200, andthe reel rotates in the bearings as a result of power transmittedthrough sprocket wheel 209 fixedly mounted to reel axle extension 222. Atrunnion mounting is thereby efiected for reel mechanism 185.

As illustrated by phantom lines in FIG. 9, as raising levers 361 arepivotally elevated, cross-bar 364 is likewise elevated, and dependingbracket members 200 swivel upwardly thereby lifting housing 200 and reelmechanism 185.

Linkage means 372 is provided whereby levers 361 are pivoted upwardly toelevate reel mechanism and housing 202 and thereby throw weight upon thewheel axle 25 and tires 24 supporting same.

Linkage means 372 comprises an actuatable bar 374 to one end of which aball-crank member 376 is pivotably attached. The apex of ball-crankmember 376 is pivotally attached to frame member 22 that is disposedbelow levers 361. Leg 378 of ball-crank member 376 extends forwardly offrame member 22. At its forward end, a connecting rod 380 connectsball-crank member 376 to the one lever 361 on the left side of machine20 as viewed in FIG. 9.

The rear end of actuatable bar 374 is attached to a manually-operablelever means 382 that is readily available to the operator of vehicle 20.Lever means 382 comprises a hub 384 to which bar 374 is pivotallyattached, a hand grasping lever 386 extending upwardly from hub 384 anda pivotable link 388 fixed to hub 384 and extending down to frame member22 and pivotally attached thereto.

It will be observed from the phantom skeleton shown of the apparatus inFIG. 9 that the rearward motion of lever 386 causes actuatable bar 374to linearly react rearwardly. As a result, ball-crank member 376 rotatesat its apex pivotally mounted on frame member 22, thereby lifting itsleg 378 and connecting link 380. This in turn pivots both supportinglevers 361 and raises crossbar 364 upwardly. Consequently, the entirereel mechanism 185 and housing 202 are swung up off the ground.

A spring means 390 cooperating with bar 374 through any one of a seriesof apertures 392 in hub .384- is provided to resiliently control theamount of weight that housing 202 and reel mechanism 185 apply againstground. As shown in FIG. 9, spring means comprises a spring 393 attachedto a portion of frame 22 on superstructure 406 (FIG. 1) at its rear end,and is connected at its front end to hub 384 preferably via a connectinglink 394. The resilient control is varied by attaching bar 374 to anyone of the series of apertures 392 in hub 384. By connecting bar 374 toan aperture 392 that is linearly closer to frame member 22 as viewed inFIG. 9, the resiliency of spring 393 relieves to a greater degree theweights of housing 202 and reel mechanism 185 upon grass or ground.

STEERING Means for steering machine 20 is efficiently and effectivelyrealized by structure illustrated in FIG. 2. A steering column 401, towhich a steering wheel 402 is mounted in a customary way, is suitablymounted to a casing 404 (FIG. 1) of superstructure 406 and is connectedto a vertically aligned rod 408, suitably supported (not shown) onhorizontally aligned spaced frame elements 410 welded to frame 22,through a universal element 412, in a customary manner. A pinion gear414 transmits the rotation of steering wheel 402 to a spur gear 416mounted at one end of a second rod 418. At the other end of second rod418, a pinion gear 420 is fixedly mounted and which meshes with a spurgear 422 fixedly mounted on an arm 424 secured to one end of a flatbracket member 426. The other end of bracket member 426 is connected toone end of a lever 428 by means of a connecting rod 430 generallydisposed rearwardly of mower 20. The other end of lever 428 is fixedlymounted by means of a stud 432 toan inverted U-shaped bearing support434 for rear wheel and tire 24. It is readily apparent from anobservation of FIG. 2 that as steering wheel 402 is rotated in thedirection shown by the arrow associated therewith, fiat bracket member426 is forced to rotate in the manner shown by its arrow thereby pullingforward connecting rod 430 and rotating lever 428, as shown by theirrespective arrows. Consequently, tire 24 turns with U-support 434 toprovide a right movement for lawnmower 20. A left movement of lawn-moweris provided, in a similar manner, when steering wheel 402 is rotated ina direction opposite to its associated arrow.

A rigid frame 440 welded transversely across open frame 22 is providedfor rotatably supporting stud 432 centered therethrough. An operatorsseat 442 is suitably mounted on frame 22, as shown in FIG. 1, over theheretofore described steering means for the purpose of providingimmediate ground traction to rear tire 24 when the operator of thevehicle sits thereon.

In the operation of machine 20, engine 21 is started in a conventionalmanner. A pivotal accelerator foot pedal(not shown) is suitably mountedon one of the foot rests 450 (FIG. 1) and is connected in a usual mannersuch as by wire linkage leading to the throttle and carburetor, etc., ofengine 21. To propel machine 20 across ground, transmission is engagedinto one of the three gears, low, high or reverse, and thereafter thefoot pedal depressed to throttle engine 21. It should be noted that thecombination of an automatic clutch 28 and transmission 30 provides for asafety advantage wherein machine 20 does not move although a gear isengaged but the foot pedal is not depressed and engine 21 is idling, thereason being that automatic clutch 28 as distinguished from afriction-type clutch is controlled by the engine r.p.m. or torquedeveloped in its drive shaft which is in turn controlled by the footpedal.

To provide for high speed movement of machine 20, lever 97 is pivoted onball 115 so that shifter fork 53 is advanced forwardly on crankshaft 49by means of lever end 96 engaging recess 95 in sleeve 92 on arm 86,whereby combination member 51 engages and locks upon driving clutchmember 47 fixedly mounted to shaft which rotates with the speed of thedriveshaft (not shown) of engine 21. Consequently shaft 49 obtains thesame r.p.m. as the engine speed, and same is transmitted, as shown inFIG. 8, to axle 25 and tires 24.

To provide for a relatively low speed forward of machine 20 lever 97 ispivoted on ball 115 so that shifter fork 66 is advanced forwardly onshaft 49 by means of lever end 96 engaging recess 98 on arm 87, wherebylow gear 65 meshes with idler cluster gear 70 about shaft 71. Since gear70 is mounted with gear 74 on sleeve 73 about shaft 71, and gear 74 isin continuous mesh with M.D. gear on shaft .35, gear 65 and shaft 49rotate in the same direction as shaft 35, however at a slower speedbecause of gearing ratios of the involved gears. Cons quently, the powerto axle 25 and tires 24 is less, and forward movement of machine 20 isslower.

To provide for reverse movement of machine 20, lever 97 is pivoted onball so that shifter fork 53 advances rearwardly on crankshaft 49 bymeans of lever end 96 engaging recess 95 of sleeve 92 on arm 86, wherebygear 80 on combination member 51 meshes with reverse idler gear 83. Gear'83 bushingly mounted on fixed reversing shaft 81 is rotatingcontinuously as a result of its being in mesh with cluster gear 70.Consequently, when gear 80 meshes with gear 83, a reverse direction ofrotation to that of shaft 35 is imparted to crankshaft 49 which in turntransmits reverse motion to machine 20 through the power train shown inFIG. 8 to tires 24.

To provide for transmission of power to reel mechanism 185, lever 168 ispivoted about pin 170 so that shifter fork 159 with arm 162 advancesrearwardly on shaft 143 by means of the tang (not shown) on the end oflever 168 engaging groove 171 of arm 162, whereby driven clutch member148 engages driving clutch member of combination member 140 that alsocarries gear 142 continuously in mesh with and rotating with M.D. gear45 when the latter is rotating. Combination member 140 is mounted on abushing (not shown) about shaft 143 so that power from shaft 35 throughM.D. gear 45 can only be transmitted to shaft 143 when members 150, 148engage the lock as a result of the rearward shifting of shifter fork159. Consequently, bevel gear 151 keyed to shaft 143 rotatively reacts,as does bevel gear 152 to meshing bevel gear 151, and as does s.p.o.shaft 155 formed integrally 'with bevel gear 152. Power from shaft 155is thence transmitted to reel mechanism in accordance with the chain andsprocket power train illustrated in FIG. 8.

It should now be apparent that the reel blades can be actuatedindependently of motion of machine 20, by the manipulation of lever 168.The r.p.m. of shaft 35 governs the speed of the reel blades, and thedistinct advantage of the combination of the immediately foregoingdescription of gearing to shaft 155 and an automatic clutch 28 is thatthe reel blades do not rotate at idle speed of engine 21, since clutch28 is controlled by a higher engine r.p.m. or torque developed in itsdrive shaft which is in turn controlled by the operators foot pedal. Onthe other hand, lodgement of an object between the bed knife means 275and a reel blade or blades causes cessation of travel of machine 20because of slippage occurring between automatic clutch 28 and drum 29and thereby not rotate shaft 35 attached to drum 29. After disengagingclutch members 148, 150 on shaft 143 by manipulating shifter fork 159 onlever 168, removal of such object may be had in complete safety whileengine 21 continues to run.

It should now be apparent that whenever the operators foot is removedfrom the engines control pedal, the r.p.m. of the shaft of engine 21drops below the necessary speed at which automatic clutch 28 engages orfirmly grips drum 29. Consequently, even though lever 97 is engaged withits gearing components in high, low, or reverse, machine 20 stops.Likewise, the reel blades no longer rotate should lever 168 engage itsgearing components and the operators foot pedal is not depressed (engineidling, i.e.).

The three-point-to-ground suspension provided by tires 24, with but oneof such tires disposed at its rear, assures that tractor or machine 20hugs ground contour, particularly in the area forward of engine 21 atwhich reel mechanism is located. It is clear, however, that suchsuspension falls short of inclusion of reel housing 202 and mechanism185 as a result of their free or floating position upon ground surfaceas a result of the trunnion mounting provided for such forwardlydisposed elements.

Housing 202 including walls 227, 228 and a rear wall 455 (FIG. 1)suitably attached thereto provides for containment of cut grass and thelike. As such grass is swept up by efficient shearing action, itcompletes a loop directed forwardly of machine 20. Heavier or lengthiercut grass fragments re rn to the cutting action of reel blades and 1 7bed knife by falling into the reel. This motion is compounded and cycledcontinuously with large grass fragments not capable of falling below bedplate knife means 275. Consequently, a highly effective fragmentarycuttingup of grass regardless of rank or massiveness is achieved. Theenclosure provided by housing 202 further eliminates danger of flyingstones, sticks, etc. that are slung indiscriminately rearwardly of thereel blades and knife therefor whose cooperation may cause such flying.

The operation for the steering mechanism illustrated in FIG. 2 anddescribed above is evident therefrom.

Pursuant to the requirements of the patent statutes, the principle ofthis invention has been explained and exemplified in a manner so that itcan be readily practiced by those skilled in the art, suchexemplification including what is considered to represent the bestembodiment of the invention. However, it should be clearly understoodthat, within the scope of the appended claims, the invention may bepracticed otherwise than as specifically described and exemplifiedherein, by those skilled in the art, and having the benefit of thisdisclosure.

Therefore, what I claim to be patentably novel is:

11. A transmission comprising a main drive shaft adapted for engagementwith an engine drive shaft and having thereon a rotatable combinationmember including a main drive gear and driving clutch member,

power output means in axial alignment with said main drive, shaft andhaving mounted thereon a) an axially slidable second combination memberincluding a reverse gear and jaw means for engaging said first mentionedclutch member on said main drive shaft, and

(b) an axially slidable low gear on said power output means,

an idler gear in continuous mesh with said main drive gear,

a cluster gear rotatable with said idler gear,

said idler and cluster gears mounted off-center of and parallel to saidmain drive shaft,

a reverse idler gear rotatable off-center of and parallel to said maindrive shaft and in continuous mesh with said cluster gear,

a first means for axially shifting forward said second combinationmember on said power output means whereby said jaw means and drivingclutch engage each other thereby providing for high gear transmission,

said first shifting means also axially slidable rearwardly whereby saidreverse gear meshes with said reverse idler gear thereby reversing thedirection of rotation of said power output means to that of said maindrive shaft,

low gearing means axially slidable on said power output means,

a second means for axially shifting said low gearing means to mesh suchgearing means with said cluster gear thereby providing for low geartransmission,

power take-off means coupled to said main drive shaft gear whereby powerfrom an engine drive shaft is directly transmitted thereto irrespectiveof engagement of said transmission in high, low or reverse gear, andcomprising a take-off shaft in parallel relation to said main driveshaft,

a take-off gear freely rotatable on said take-off shaft and incontinuous mesh with said main drive shaft gear,

a driving jaw clutch rotatable with said take-off gear,

a driven jaw clutch slidably mounted on said take-01f shaft androtatable therewith and in facing position to said driving jaw clutch,

gear means rotatably mounted on and rotatable with said take-off shaft,

driving means co-acting with said gear means and providing fortransmission of power from said main drive shaft, and

a third means for axially shifting said driven jaw clutch member intoengagement with said driving jaw clutch and take-off gear,

whereby said take-01f shaft rotates thereby actuating said drivingmeans.

2. The transmission of claim 1 including an operable lever means forcooperating with either said first or second shifting means to providefor a high or low transmission engagement.

3. The transmission of claim 1 including operable lever means forcooperating with either shifting means mounted on said, main drive shaftand operable lever means for cooperating with said third shifting meansto provide for transmission engagement between the engine shaft and saiddriving means.

4. The transmission of claim 1 in which said driving means comprises ashaft and a bevel gear securely mounted thereon, said bevel gear meshingwith said gear means.

5. A transmission mechanism comprising main drive shaft means,

a shaft off-center to said main drive shaft means,

a take-off gear freely rotatable about said shaft and continuouslymeshing with said main drive shaft means,

clutch means rotatable with said take-off gear,

axially slidable clutch means fixedly mounted on said shaft and adaptedto engage said clutch means,

a pair of cooperating bevel gears, the first being rotatable with saidshaft,

an output driving shaft coupled to the second of said bevel gears, and

means for axially shifting said axially slidable clutch means intoengagement with said clutch means,

whereby power from said main drive shaft means is transmitted to saidoutput driving shaft.

6. The mechanism of claim 5 in combination with automatic clutch meansconnected to said main drive shaft means.

7. The mechanism of claim 6 in which said automatic clutch meanscomprises a drum and a clutch, said clutch drum attached to said maindrive shaft means and rotatable therewith, and said clutch being fixedlysecured to the engine drive shaft,

whereby upon attainment of a predetermined torque developed in or ofhighervalues in the r.p.m. of the engine drive shaft, said clutch firmlyengages said drum thereby transmitting the speed of the engine shaft tosaid main drive shaft means.

References Cited UNITED STATES PATENTS 2,055,770 9/ 1936 Manville74-343X 2,276,000 3/ 1942 Stumpf 7415 .86 2,316,503 4/194'3 Curtis74'15.86X 2,355,710 8/1944 Dodge 192103 (B) 3,046,813 7/1962 Bixby74-665 LEONARD H. GERIN, Primary Examiner U.S. Cl. X.R.

